“Fatigue Analysis of a Harsh Environment FPSO using …irvineeng.com/images/Irvine Eng Fatigue...
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“Fatigue Analysis of a Harsh Environment FPSO using SESAM”
Scope of Presentation
• Typical harsh environment FPSO
• Identification & classification of fatigue sensitive locations
• Outline of analysis procedure
• Example using SESAM
• Performance
Terra Nova – Harsh Environment FPSO
Key Questions!
• What locations ?
• What analysis procedure ?
• What software ?
• What model ?
• What vessel condition ?
• How is procedure implemented ?
• How can performance be improved ?
Fatigue Sensitive Locations
Main hull
Mooring system
Flare tower Crane pedestals
Openings Module supports
Hopper knuckles
Turret structure
Main bearing points Mooring line connection
Shell connections
DnV Classification Note CN30.7
Design Wave Approach Sec. 5.5
Equivalent Long Term Stress Distribution (Weibul
param.), Sec. 5.2
Long Term Stress Distribution, Sec. 3.2
FE model of detail, Sec. 6.3-6.6
Stress Component based Stochastic Fatigue Analysis
Sec. 5.6
Simplified Analysis Direct Analysis
Load Response Sec. 4.2-4.4 Load Response Sec.5.2 Load Transfer Function. Sec. 5.3
2.2 Stress Components Interchangeable Results
FE model of ship, Ch.6
SCF: K-factors,Ch.7 Interchangeable Results
Combination of Stresses, Sec. 3.4-3.4 Local Stress Transfer Functions
for stress components Sec. 5.4
Full Stochastic Fatigue Analysis Sec. 5.7
Fatigue Damage Summation:
Summation of damage contributions from each wave period/ship heading combination for each sea state in the
wave scatter diagram
Fatigue Damage Calculation, Sec. 2.1
Software
• Repetitive hull geometry makes it ideally suited to superelement approach.
• Sub-modelling can be used where necessary. Hot spots do not have to be known a priori.
• Totally integrated solution. All pre- & post- processors necessary for complete analysis are available.
• Committed software support
SESAM is the Preferred Tool for Fatigue Analysis of FPSO’s because . . .
Hydrodynamic Analysis Model Hull Form Example
Structural Analysis Model Moonpool Fatigue
Structural Analysis Model Mid-ship and Wingtank Superelements
Structural Analysis Model Moonpool Superelements
Structural Analysis Model Turret Superelement
Structural Analysis Model Typical Mid-ship Section Showing Scantlings
Implementation
POSTRESP Calculate fatigue lives
POSTFEM Extract stresses Review behaviour Select SN curves
Stage 1
Obtain vessel mass and geometry data
Obtain moonpool geometry data
Establish locations to be analysed & level of modeling detail
WADAM Create motions model
Stage 3
PREFEM Create Geometry model
WADAM Create RAO’s
PREFEM Apply loads & boundary conditions
SESTRA Obtain Unit Stresses
Stage 4 Stage 2
PRESEL Assemble superelements
PREPOST Create results database
Implementation
1 2 3 4 5 6 7 8
Apply Unit Load Cases
Multiply by ‘Wadam’ Transfer Functions H(ϖ/υ)
Interpolate to Obtain Principal Stresses Pmin & Pmax
Combine to Obtain Principal Stress Transfer Functions
MO
OR
ING
, Fx
MO
OR
ING
, Fz
MO
OR
ING
, My
VER
T A
CC
,
N
a z
. .
HO
RZ
AC
C N
a
x . .
BEN
DIN
G M
OM
ENT,
M B
mt
EXT,
PR
ESSU
RE,
P ex
t
INT,
PR
ESSU
RE,
P in
t
A1 A2 A3 A4 A5 A6 A7 A8
A H (ϖ/υ) A H (ϖ/υ) 2 2 A H (ϖ/υ) 3 3 A H (ϖ/υ) 4 4 A H (ϖ/υ) 5 5 A H (ϖ/υ) 6 6 A H (ϖ/υ) 7 7 A H (ϖ/υ) 8 8
H (ϖ/υ)
SEST
RA
STA
GE
3
PO
STF
EM
S
TAG
E 3
P
OS
TRE
SP
S
TAG
E 4
1 1
σ
Implementation P
OS
TRE
SP
S
TAG
E 4
Tz (secs) X
Stress
Spreading Function
Principal Stress Response Spectrum
Assume Rayleigh Distribution
Establish Probability of Occurrence
Σ for all points in scatter diagram
Total Distribution Average Cross Rate = T z
Select S-N Curve and Calculate Fatigue Life
No of Cycles
Total No of Cycles
σ
σ σ
σ
Rep
eat f
or a
ll P
oint
s in
Sca
tter D
iagr
am H (ϖ/υ)
2 σ
ϖ
HS
(m)
Fatigue Analysis
• Selection of S-N curve dependent on:
– Direction of principal stress relative to weld
– Mesh size
– Weld type
– CP protection
• SCF’s due to weld notch effect and local geometry
• Weibull or Rayleigh calculation
• Fracture mechanics
• Safety factors
Fatigue Analysis Example
R60 Cope hole
R60 Cope hole
Fatigue Analysis Example
Detailed Mesh at Location F
Fatigue Analysis Example
Location F Maximum Principal Stress S2
Fatigue Analysis Example
Location F Maximum Principal Stress S2
Fatigue Damage Calculations S-N curve: DEn-C-29
Fatigue life:= 1 / [8.499 E-3] = 115 years Fatigue Safety factor = 2 [dry, critical, inspectable & repairable] Target fatigue life = service life x safety factor = 25 x 2 = 50 years Hence, OK
No Description Damage per annum Ranking 1 Heave acceleration 4.324 E-16 3 2 Surge acceleration 7.182 E-18 5 3 Mooring force, Fx 3.385 E-16 4 4 Mooring Force, Fz 1.555 E-22 6 5 Mooring moment, My - - 6 Bending 7.741 E-3 1 7 External pressure 2.848 E-10 2 8 Internal pressure - -
Total 8.499 E-3
Performance
• Structural FE model 400,000 D.O.F.
• Analysis run on UNIX platform took 1.5 hours C.P.U. using new solver. Typically, SESTRA results file was 0.2 GBytes, POSTFEM database was 2 Gbytes.
• Analysis optimised by varying superelement hierarchy. Best performance achieved when minimum number of supernodes were carried forward to higher levels of hierarchy.
• Superelement approach ideally suited to FPSO fatigue problem. Solution times are faster (compared with analysis of one large model) and model can be built by team.
Use of F.E.A. at Irvine Engineering
Thank You
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